Fluid transmission.



J. LEHNE.

FLUID TRANSMISSION.

APPLIGATION FILED MAY 4, 1910.

1,042,696. Patented oen. 29, 1912.

6 SHEETS-SHEET 1 J. LEHNE.

FLUID TRANSMISSION. APPLICATION FILED MAM, 1910.

1,042,696. Patented 001129, 1912. j A

5 SHEETS-SHEET 2.

, J. LBHNE.

FLUID TRANSMISSION.

APPLICATION FILED MAY 4, 1910.

1,0425696. Patented 0015.29,1912.

5 SHEETS-SHEET 3.

J. LBHNE. FLUD TRANSMISSION.

APPLICATION FILED MAY 4, 1910.

Patented Oct. 29, 1912. mi y v MENTS-SHEET 4.

J. LEHNE.

FLUID TRANSMISSION.

APPLIOATION FILED MAY 4, 1910.

. 1,042,696. Patented @15.29, 1912.

5 SHEETS-SHEET 5.

UNTED STATES PATENT FFICE. JOSEPH LEHNE, OF CHARLOTTENBURG, GVERINIIANY, ASSIGNOR T0 INTERNAKTKSNALE ROTATIONS-MASCHINEN -GESELLSCHAFT M. B. H., 0F BERLIN, GERMANY.

FLUID TRANSMISSION.

Specification of Letters Patent.

Patented oet. 2a, isis.

Application filed May 4, 1910. Serial No. 559,353.

T o all whom t may concern Be it known that l, JOSEPH LEHNE, engineer, a subject of the Grand Duke of Hesse, residing at Charlottenburg, Germany, have invented certain new and' useful improvements in Fluid Transmission; and I do hereby declare the following to be a full, clear, and exact description of the invention, such as will enable others skilled in the art to which itappertainsto make and use the same, reference being had to the accompanying drawings, and to letters or figures of reference marked thereon, which form a part of this specification.

My present invention relates to rotary machines, and more particularly to that class of suoli machines used for the transmission of liquid or as power devices operated by a. liquid, or both, as will hereinafter be more particularly described and claimed.

The main feature of this invention relates to that type of rota-ry machines in which any number of slides acting as pistons are moved in radial slots or grooves in a roter oi' drum that rotates in a casing forming working spaces between the end surfaces or the circumferential surface of said drum a-nd the end surfaces or internal circumferentia'l surface of the casing. Such machines are of two general types, theaxial type, wherein the slides move in their slots in a direction parallel to the axis of the drum, and the radial type in which the slides move in their slots radially tothe axis of the drum. y

The working spaces have a varying width,

as is well known; the size of the active working space, and, in the case of a pump, its capacity, `will depend, under otherwise identical conditions, ony the dii'fereiices in the 'width at the various points of saidspaces, and not on `their total size.

In the present invention, a controlling of the capacity of the rotary machine is obs,

slides, and 'i in conjunction therewith in the axial type of rotary machine illust-rated, also by displacing the drum in which the slides are mounted, thereby varying the width of Zthe working spaces swept by the slides, as will more fully appear hereinafter. By a suitable combination of two working spaces a perfect compensation of pressure may be obtained as well asa delivery in eitherdirection without requiring the reversal of the direction of rotation.

In the drawings in which like parts are similarly designated, I have chosen to show' one forni of apparatus embodying my inventiori as applied to a fluid transmission, specifically, the primary part or pump of a hydraulic change or reversing gear for power driven vehicles or the like, in combination with a motor of known type serving as a secondary moto-r that furnishes the direct or driving power for the vehicle.

Figure l is a vertical, longitudinal section of one form of rotary machine embodyingmy invention, the section of the motor M being taken on the line I-K `Fig. 3. Fig. 2 is a section taken on line A-B of Fig. l, the rotor or drum being rotated 450'. 4Fig. 3 is a vertical, transverse section of the secondary rotary motoron the line C- Fig. l. Figs. 4, 5 and 6 are developed diagrams illustrating the operation of the rotary machine or pump. Figs. 7 and 8 are, respectively, elevation and plan showing a modified forni of the lever mechanism for effecting the movement of the rotor or drum. Figs. 9 and 10 are developed diagrams showing two modifications of the rotary machine. Fig. ll is a perspective view part-ly iii section,.showing the interior of the lining at one end and the adjustable abutment. Fig. 12 is a perspective view of the radially grooved or lslotted rotor.

The rotor or drum 1. of the rotary machine lact-ing as a pump P, Figs. l, 2, 4, 5

and 6, is provided with a plurality of radialv grooves, in this particular instance with four, in each one of which is fitted a piston slide 2 (a, b, c, d).

The rotor or drum is mounted in a cylindrical casing comprising, as shown in this particular instance, an outer sliellfa an inner shell b and a two-part lining c, c'. The

space between theouter shell a and inner shell b is divided into two portions by webs, herein indicated as vertical Webs e, Fig. 2, dividing the space between two shells into two circulating chambers, .the suction and delivery 'chambers 9 and 9a hereinafter referred to. The two parts of the lining are held distanced from one another by means ot' a ring cl of lesser thickness than the lining and which is flush with -the outer surface thereof. That portion of the space between the adjacent ends of the parts c and c of the lining and not occupied by the spacing ring rl forms a cam groove 6 in which rollers 5 on the slides 2 travel, whereby said slides are reciprocated.

The making of the lining in two parts permits the accurate shaping of the adjacent ends andl facilitates the formation of the groove. This particular feature may be Varied to suit the conditions of manufacture; the lining maybe omitted altogether and the groove formed in the inner shell b or otherwise, the essential feature being the presence of a cam or cams to impart. proper reciprocation to the slides in the radial slots of the rotor during the rotation of the latter.

nto the ends 3 and 3 of the casing that are opposite the ends of the rotor or drum 1, are arranged the stationary, but axially adjustable abutments 4 and 4 with which the slides coperate to effect the movement of the liquid.

The slides 2 are guided in such a manner by their rollers 5 in the cam groove formed between t-he sections c and c of the lining, that they will, in their one eXtreme position, be in Contact with one end 3, and in their other extreme position be in contact at their opposite ends with the other end 3.

The rotor or drum 1 is provided with a spindle 23 rigidly connected thereto and vsuitably driven. This spindle is supported in sleeve bearings 24 andv 24 which are fitted between collars 36 and 36 on the spindle. On the bearing 24 is fitted a ring 25 engaged by a lever 26 connected by a link 27 to a lever 28 designed to be operated by hand. A cam 29 fitted to lever 28 limits the stroke of the link 27 by acting as a stop at the terminal positions of said link.

On the sleeve bearings 24 and 24 are guided sleeves 31 and 31 respectively, under the action of springs 30 and 30 in such a manner that a certain relative movement between the two sleeves 24 and 31, and 24" the position shown in Fig. 1, where said drum is in contact with the end 3', to the a pressure space, 7 or 7 or both 7 and 7',

depending upon the position of the rotor in the casing. These pressure spaces communilcate with delivery ports 12 and 12', and be hind each abutment there is a suction space 8 or 8 or both, communicating with admission ports 13 and 13. In other words, each abutment is between an admission and delivery port formed by an opening through the lining and inner shellFigs. 1, 2 and 11. Then the rotor or drum 1`is in either of its extreme positions Figs. 4 and G, either the pressure spaces 7 and 8 or 7 and 8 are reduced to zero and only one end of the rotor is elfective. The delivery ports discharge therefore into the delivery chamber 9 Fig. 4 or9a Fig. 6, while the suction ports receive fluid from the suction chamber 9a Fig. 4, or 9, Fig. 6.

' The rotor or drm 1 is provided with i through passages 11 (a, b, c, d) one between each two neighboring piston blades so that the pislon'blades 2 and passages 11 alternate with one another, Figs. 2 and 12. These passages 11 through the rotor or drum 1 connect the delivery and admission spaces 7 and 8, and 7 and 8 at the two ends of the casing when the position of the rotor is such as to permit the presence of the spaces at both ends of the rotor. One of their objects is to equalize the hydraulic pressure at both ends of the rotor.

The pressure spaces 7 and 8 for example in Fig. 5 not only communicate with each other inside t-he easing through the passage 11c but also outside the casing throughthe discharge port 12 at one end, and the admission port' 13 on the other end, both of said ports communicating with the chamber 9 and extension 10 of chamber 9. rllhis chamber 9 then acts as a by-pass in conjunction with 11C. In like manner the pressure spaces 7 and 8 not only communicate with each other inside the casing through t-he passage 11a, Fig. 5, but also outside the casing through the discharge port 12 at one end, and the inlet port 13 at the other end of the casing connected by chamber 9aL and its eX- tension 10a. Chamber 9a also acts as a bypass between these ports with 11a. Thus it will be seen as each pair of adjacent piston blades 2 take up their positions, during the rotation of the rotor or drum 1, immediately behind or in front of the stationary abutments 4, 4', they will in the position shown in Fig. 5, connect the inlet and discharge ports through chambers 9 and 9a now acting as by-passes, and consequently the rotary machine in this particular position is ineffective or runs idle. liquid at this time will be as follows, admislsion at port 13 moved by blades 2 through delivery space 7 to discharge ort 12, chamber 9 to inlet port 13 and a mission space 8 at the other end of the rotor thence back through port l2', chamber 9, port 13, back to 8. The movement of the rotor 1 toward the abutment 4 causes a throttling of the ports 7 and 8', consequently the quantity of liquid partaking in the idle circulation, or passing through the chambers 9 and 9EL acting as by-passes will decrease inaccordance with the size of the working -spaces until these two ports are completely closed, as indicated in the position Fig. 4, wherein the abutment 4 has been forced against the stress of its spring 30 iush with the end of the casing or cylinder which corresponds to the position shown in Fig. l. In this position the admission and discharge ports at i the right hand end of the cylinder F ig.\1,

(lower portion of Fig. 4) are completely closed by the rotor l, and the abutment 4 projects into the cylinder or casing to its full extent, the same as in Fig. 5. The liquid is admitted or aspirated at 8 through admission port 13 on ore side of abutment 4 and is discharged byjthe blades 2 through the port 12 on the other side of the abutment i, 4, the chambers 9 and 9a will now act purely as admission and discharge chambers, while the passage 11 will `still be effective for equalizing the pressure on both ends of the rotor. The volume of liquid moved will correspond to the extent of the projection of abutment 4 from the end wall of the casing, will be from 10a to 10, Fig. 4.

Fig. 6 is just the opposite of Fig. 4, here the other end of the pump P works, and the same quantity of liquid as in Fig. 4 is moved from 10 to 10, reversed in direction.

Between the positions shown in Figs. 4 and 5 and 6 and 5 there are any number of intermediate positions. Atall intermediate positions between those shown in Figs. 4 and 5 the active working space or chamber is greater on the upper than on the lower side, because the abutment 4" advances from the face of the end of the casing, urged by its spring to follow up the shifting of the rotor, while the abutment 4 remains stationary. At all these intermediate positions there is aiow, the same as in the position according to Fig. 5, from the upper space to the lower space through passage 9, but only a part of the liquid conveyed from the upper working space can be received by the lower, smaller space, while the surplus is forced od through socket piece 10 and represents the delivery proper of the pump. In the same manner the quantity of liquid flowing from the lower working space to the upper working The movement of t'heY space through passage 9a will not besutlicient to fill the upper space and the still required quantity is aspirated through socket piece 10a. The effect is similar at-the intermediate positions between Fig. 5 and Fig. 6, only here the lower space holds a larger quantity of liquid, while the upper space serves as circulating space. Here furthermore, socket piece or union 10 is the suction one, and 10a the delivery one, in other words, the direction of the delivery is reversed.

From what has been described'above it is evident that by means of my improved engine any quantity of liquid varying from zero to a maximum, within the limits of the machine, may be conveyed in either the one or the other direction. The arrangement could also be made for a conveyance in one direction only and with a working space arranged on one side only. -In such instance the only condition to be observedwould be, that the drum remains always in close contact with the abutment. However, the double sided arrangement affords the possibility of entirely relieving the pressure in .an axial direction, so that there will be n0 axial thrust. of the'rotor. This relief is obtained in the present instance by the drum being provided between each two slides with a passage 11 (11,6, c, d) through which the corresponding axially opposite sections of the Working space at each end are made to communicate, so that theA same total pressure must exist on either side. For obtaining a compensation of pressure also in the terminal positions Figs. 4`and 6, the provision may be made, that at such positions the abutment still projects a little beyond the surface of the casing, so that there remains a certain amount of play between the drum and the casing. 1t istrue, that this will` mean a small loss of eliciency corresponding to the contents of the active working space remaining at this side. The passages 11 in the drumv may also serve as passages for conducting the liquid from the pressure space' on the one v`side to the suction space on the other side, so that the chambers 9 and 9a in the casing may be dispensed with, that is,

`and downward respectively, and a part of the liquid can How from space 7 through the gap between the slide 2c and the end of the casing and also through the port 12 leading into space 7 around the outer edge of the that width included between the abntments and the ends of the rotor. It will thus be Seen that the capacity or efficiency of the pump for any one adjustment is dependent on the difference between the projections of the abutments into the working chamber.

The secondary motor M has, in the arrangement of a change or reversing gear illustrated in Figs. 1 and 3, the known form of a rotary machine, the piston drum 14 of which has a number of concentric grooves 15, say two, cut in each of its end surfaces, which groo-ves are closed at one point by fixed abutments 16, whereas the radially movable slides 17, which ordinarily also close the grooves 15, are adapted to pass the abutments 16 by means of recesses or notches 18 provided in them. The controlling ot the slides 17 is obtained by guiding their ends between equidistant curves 19, 19. In front and behind the abutment 16 an opening 20 or 20a respectively, in wall 21 leads into every groove 15 in the end of the motor drum 14 toward the pump. The passages 20 communicate with passages 9, passages 20aL with passage 9a. The communication between the grooves 15 on the other side of the drum with the same passages 9, 9a is obtained by means of axially arranged passages 22 passing through the drum between each two slides 17. The result is, that according to the direction of delivery of the pump P the motor M will revolve in one or the other direction. At the same time the speed of the motor will vary with the volume of the delivery of the pump. By the use of this mechanism on a motor driven vehicle it will thus be possible t0. drive forward or backward at any speed varying from zero to the given maximum by simply adjusting the drum 1 of the pump and its abutments 4 and 4 respectively.

The position shown in Fig. 1, corresponds to the position'shown in diagram Fig. 4, in other Words, the drum and the abutments are in their extreme position on th'e right (lowermost position Fig. 4) the abutment 4 is moved out fully, abutment 4 is moved back fully, spring 30 is compressed, spring 30 slack.

Then the lever mechanism 26, 27 28 isV turned to the left, it will move the spindle noemen ment 4 willvfollow the drum under action of spring 30 until sleeve 31 strikes against stop 32', while the abutment 4 remains stationary until drum 1 comes into contact with it. The sleeve 31 meets stop 32simu1 taneously with drum 1 meeting abutment 4, abutment 4 will now remain stationary, while abutment- 4 together with sleeve 31 is carried along by the drum, the spring 30 being compressed thereby, until all parts have reached their respective extreme position on the left.

In Figs. 7 and 8 the adjusting lever mechanism is shown in a somewhat diierent arrangement. Here, furthermore, safety valves 33, 33 are provided, through which the liquid may pass from the compression to the suction space when a given maximum' pressure is exceeded. Forthe purpose of avoiding that the abutments 4 4 are moved outward against the smaller pressure of the springs 30, 30 by the greater pressure inside the pump, the space behind each abutment communicates with the respective delivery passage adjacent thereto, z'. c., with 9 or 9fdl when they carry pressure fluid.

In the constructional form according to diagram Fig. 9, the arrangement issuch that the two abutments 4', 4 will be in close contact with the drum l in every position. The slides 2 are accordingly so dimensioned that their length corresponds to only the length of the drum. The abut-ments need no longer till up a whole quadrant, as in the arrangement shown in Figs. 1 and 6, where such was necessary so that the slide passingan abutment .might remain in close contact with the same during a suiiicient length of travel. Lastly the constructional form'according to diagram Fig. 10 represents a reversal ot' the hereinbefore described arrangements, in so far that the abutments 4, 4 are arranged on the inside, rigidly connected with a disk 34,

while the drum and each slide are separated into two members connected with each other in a rigid manner by suitable means. The slides 2 rotating with the drum are guided with their end surfaces on outwardly arranged equi-distant curved surfaces'i'35, 35. The drum 1 is axially adjustable, t-he same as in the other constructional forms, so that the working spaces lying between its two members and the stationary parts 3, 3 of the casing can be adjusted to any desired width.

Instead of combining the two working spaces in one machine, as shown in the drawings, a suitable communication between the working spaces of two separate single acting machines may be employed for the same purpose. These two machines would then be preferably arranged on the same spindle, so that they would relieve each other; they might, however, also have separate spindles and even run at ditlerent speeds.

65. 23 with the drum 1 to the left, the abutl It will be noted that the right and left .quantity of tiuid delivered by the machine.

2. In a rotary machine, the combination of a casing, a rotor havin radial grooves, slides axially movable in said grooves, means for reciprocating saidslides, a stationary abutment in said casing and projecting into the Working space between rotor and casing and adjustable as to depth of its projection into the casing, to vary the effective size of the Working chamber.

3. In a rotary machine, the combination of a casing, a rotary drum having radial grooves, slides arranged in said grooves, means for reciprocating said slides in an axial direction, an abutment in said casing projecting into the working space between the casing wall and the end face ofthe drum, means for axially adjusting said abutl ment, said drum being also adjustable axially together with said abutment.

4. In a rotary machine, the combination with a casing, a radially grooved rotor therein and a stationary abutment therein; of means to simultaneously adjust the abutment and rotor| in the casing to vary the output of the machine.v

5. In a rotary machine, the combination of a casing, a rotary drum having radial grooves, slides arranged in said grooves, means for reciprocating saidslides in an axial direction, said drum being axially adjustable, an abutment in contact with the end surfaces of said drum and means for adjusting said drum and abutment.

6. In a rotary machine, the combination with a rotary drum therein having radial grooves, slides arranged in said grooves of a length not exceeding the length of the drum, an abutment in the casing projecting into the working space formed between the casing wall and end face of the drum, means for controlling the axial movement of the slides relatively to the drum, said drum and abutment being axiall adjustable.

7. In a rotary mac ine, acasing having admission and discharge ports at each end, a radially grooved, axially adjustable ro-tor in the casing, slides axially slidable in the grooves, stationary abutments at each end of the casing adjustable to and from the ends of the rotor, and chambers each connecting an admission port at one end of the casing with a discharge. port at the other end.

cable in the grooves, an adjustable abutment with which said slides coperate and which varies the effective Working space swept by the slides to vary the delivery of the machine, and means both external of and internal ofy the machine lo eifect communication of the admission and delivery sides thereof.

9. In a rotary machine, a casing having admission.. and exhaust ports, a radially grooved, axially adjustable rotor in the casing, slides reciprocable in the grooves, Ian axially adjustable abutment with which said slides coperate and which varies the effective Working 'space swept by the slides to vary the dehvery of the machine, and means both external of and internal ofthe `machine to effect communication of the admission and delivery sidesthereof. i

10. The combination of two rotary machines, each of these machines having in combination, a .rotary drum provided with radial grooves, slides arranged in said grooves, means for reciprocating said slides, one of said machines having its drum axially adjustable, an abutment in the casing projecting into the space between the end wall of the casing and the side surface of the drum, and means for axially adjusting said abutment, the suction side of each machine being in communication with the delivery side of the other machine.

11. The combination of two rotary machines, each of these ymachines having in combinat-ion, a rotary drum having radial grooves, slides arranged in the grooves, means for reciprocating said slides and one of said machines having its drum axially adjustable, an abutment. in its casing projecting to an adjustable depth into the space between the end wall of the casing and the side surface of the drum,and means for axially adjusting said drum and abutment, the suction side of each machine being in communication with'the delivery side of the other machine.

y12. A rotary machine representing a combination of two partial machines, these machines having a casing common to both of them, a drum common to both of them in said casing, provided with radial grooves, slides arranged in said grooves, means for reciprocating said slides in anvaxial direcyim tion, said drum being axially adjustable,

abutments insaid casing projecting to an adjustable depth into the spaces between the end walls of the casing and the end surfaces of the drum, means for axially adjusting said drum and abutments, the suction side` of each partial machine being in communication with the delivery side of theother partial machine.

13. A; rotary machine having a casing, a rotary drum in said casing, said drum having radial grooves, slides arranged in said grooves, means for reciprocating said slides in an axial direction, said drum being axially adjustable, abutments projecting into the spaces between the end Walls of the casing and the end surfaces of the drum` means for axially adjusting said drum and abut-ments, said drum having an axial passage between each two adjacent slides.

14. A variable speed driving mechanism having in combination, a pump consisting of a casing, a rotary drum having radial grooves, slides arranged in said grooves, means for reciprocating said slides in an axial direction, an abutment in said casing projecting into the working space between the easing Wall and the side face of the drum, means for axially adjusting said abutment, said drum being also adjustable axially together with said-abutment., and a motor in Working communication with said pump.

15. A variable speed driving mechanism having in combination a pump consisting of a casing, a rotary drumhaving radial grooves, slides arranged in said grooves, means for reciprocating said slides in :in axial direction, said drum being axially ad.- justable, an abutment in contact with the end surface of said drum, means for adjusting said drum and abutment, and a motor in Working communication with said pump.

16. In a rotary machine, the combination With a casing having admission and dis charge ports, an adjustable, radially grooved rotor, slides movable in the grooves of the rotor, a spring-urged abutment cooperating with the ends of the slides and means to axially adjust the rotor, said abutment be Loaaeae ing displaced against the stress of itsI spring by said rotor during its adjustment.

17. lin a rot-ary machine, the combination With a casing having admission and discharge ports, a radially grooved rotor in t-he casing, slides axially movablein the rotor grooves, spring-urged adjustable abutments projecting into the ends of the casing means to limit the extent of their projection into the casing, means to axially adjust the rotor and simultaneously adjust one or the other abutment against the action of lits spring.

18. In a rotary machine, a casing, a sectional lining therefor, the opposed ends of said lining formed as cam surfaces, and means to hold said sections apart to form a cam groove between the opposed sections.

19. A variable speed and reversing mechanism having in combination rotary units action as pumps, said units having a common casing, a. drum common to both of them in said casing and provided with radial grooves, slides arranged in said grooves, means for reciprocating said slides in an axial direction, said drum being axially adjustable, abut-ments in said casing, projecting to an adjustable depth into the spaces between the end Walls of the casing and the end surfaces of the drum, meansI for the suction side of each unit being in communication with the deliveryside of the other, and a motor in Working communication With said units.

In testimony that I claim the foregoing as' my invention, I have signed my name in presence of two subscribing Witnesses.

JOSEPH LEHNE. Witnesses:

AUGUST TRAUTMANN, HENRY HAsrER.

Aaxially adjusting said drum and abutments, 

